CN212297550U

CN212297550U - Stepless speed variator

Info

Publication number: CN212297550U
Application number: CN202021616318.XU
Authority: CN
Inventors: 罗杰
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-08-06
Filing date: 2020-08-06
Publication date: 2021-01-05
Anticipated expiration: 2030-08-06

Abstract

The utility model discloses a continuously variable transmission belongs to derailleur technical field. The stepless speed changer comprises a shell, wherein a first installation cavity is arranged in the shell; the differential is arranged in the first mounting cavity, the input end of the differential extends out and is connected with one end of the shell in a shaft mode; the planetary speed reducer is arranged in the first mounting cavity, and one end of the planetary speed reducer is connected with the output end of the differential mechanism; the hydraulic coupler is installed in the first installation cavity, and one end of the hydraulic coupler is connected with the other end of the planetary reducer; torque controller, torque controller installs first installation intracavity, and torque controller's one end is connected with hydraulic coupler's the other end, and torque controller's the other end runs through and extends the other end of casing, and this derailleur output capacity is very strong, and the torque converter is nimble to be controlled portably, can adapt to various operating modes and use.

Description

Stepless speed variator

Technical Field

The utility model relates to a derailleur technical field, more specifically the utility model relates to a continuously variable transmission that says so.

Background

The transmission is one of the core parts of the automobile and is mainly used for changing the rotating speed and the torque of an engine. The transmission ratio can be changed by using the speed changer, and the functions of reversing driving or interrupting power transmission and the like are realized. The speed changer comprises two parts, namely a speed changing transmission mechanism and an operating mechanism. The speed-changing transmission mechanism is mainly used for changing the numerical value and the direction of rotating speed and torque, and the operating mechanism is mainly used for controlling the transmission mechanism to realize the change of the transmission ratio of the speed changer. Namely, the gear shifting is carried out to achieve the aim of torque conversion.

The Manual (MT) operation of the existing transmission is complex, the gear shifting and pause feeling are obvious, and the driving technical requirement is high. Automatic (AT) structure is complicated, and the branch art content is high, and transmission efficiency is low, and the oil consumption is high. The stepless speed change (cvT) transmission steel belt bears limited torque and limits output torque, and the steel belt and the cone pulley have high cost and high maintenance price.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a continuously variable transmission to solve the technical problem who exists among the background art.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

a continuously variable transmission comprising: the device comprises a shell, a first mounting cavity and a second mounting cavity, wherein the first mounting cavity is arranged in the shell; the differential is arranged in the first mounting cavity, the input end of the differential extends out and is connected with one end of the shell in a shaft mode; the planetary speed reducer is arranged in the first mounting cavity, and one end of the planetary speed reducer is connected with the output end of the differential mechanism; the hydraulic coupler is installed in the first installation cavity, and one end of the hydraulic coupler is connected with the other end of the planetary reducer; and the torque controller is installed in the first installation cavity, one end of the torque controller is connected with the other end of the hydraulic coupler, and the other end of the torque controller penetrates through and extends out of the other end of the shell.

Further, the differential includes: the hydraulic coupler comprises a first input shaft, a first bearing, a first planet carrier, a first meshing transmission component, a second bearing and a connecting shaft, wherein one end of the first input shaft penetrates through and extends out of one end of the shell, the other end of the first input shaft is connected to the first planet carrier, the first meshing transmission component is arranged on the first planet carrier, one end of the connecting shaft is connected to the first meshing transmission component, and the other end of the connecting shaft penetrates through the planetary reducer and is connected with the second bearing arranged on the hydraulic coupler.

Further, the first meshing transmission part comprises a first planetary gear and a second planetary gear which are oppositely arranged; first bevel gear and second bevel gear that sets up relatively, first planet carrier includes installation end and lower installation end, and has formed between last installation end and the lower installation end and has placed the chamber, first planetary gear hub connection is at last installation end, second planetary gear hub connection is at installation end down, first bevel gear sets up and is placing the intracavity, the one end and the first bevel gear fixed connection of connecting axle, and the second bevel gear is equipped with the chamber of dodging that runs through along the axial, the tip at planetary reducer is connected to the second bevel gear, and the connecting axle runs through and dodges the chamber setting, first planet gear meshes with first bevel gear and second bevel gear respectively, second planet gear meshes with first bevel gear and second bevel gear respectively.

Furthermore, the planetary reducer comprises an inner gear ring and a second meshing transmission part, a second mounting cavity is formed in the inner gear ring, one end of the inner gear ring is a closed end, the other end of the inner gear ring is an open end, a through hole for a connecting shaft to penetrate through is formed in the closed end, the second meshing transmission part is arranged in the second mounting cavity, the connecting shaft penetrates through the second meshing transmission part, and the second meshing transmission part is meshed with the inner wall of the second mounting cavity; the open end is connected to the end face of the hydraulic coupler.

Furthermore, the second meshing transmission part comprises a first-stage reduction gear set, a second-stage reduction gear set, a third-stage reduction gear set, a second planet carrier, a third planet carrier, a fourth planet carrier and a cam, the first-stage reduction gear set is fixedly connected with the connecting shaft, the first-stage reduction gear set transmits power to the second-stage reduction gear set through the second planet carrier, the second-stage reduction gear set transmits power to the third-stage reduction gear set through the third planet carrier, and the third-stage reduction gear set transmits power to the cam through the fourth planet carrier.

Further, the hydraulic coupler includes: the mounting disc, be equipped with first division board in the mounting disc, mutual sealed interior installation cavity and outer installation cavity are separated into with the mounting disc to first division board, install the hydro-cylinder that a plurality of equidistant settings in the outer installation cavity, the flexible end of hydro-cylinder is sealed to run through the first division board and sets up including the installation cavity, the cam sets up including in the installation cavity, and the cam rotates when contacting with the flexible end of each hydro-cylinder respectively, and ring gear and interior installation cavity are linked together.

Further, hydraulic coupler still includes that the annular leads oil pipe and returns oil pipe, and the lateral wall that goes out oil pipe of every hydro-cylinder and run through outer installation cavity leads oil pipe with the setting at the outside annular of outer installation cavity and is linked together, and the oil pipe is led with the annular to the one end that returns oil pipe is linked together, and the other end that returns oil pipe is linked together with the lateral wall of outer installation cavity, and returns oil pipe and runs through the torque controller setting.

Further, the torque controller comprises a first coupler output shaft and a second coupler output shaft, a second partition plate is arranged in the shell, one end of the first coupler output shaft penetrates through the second partition plate to be connected with the mounting disc, the first coupler output shaft and the second partition plate are connected through a third bearing, a third mounting cavity is formed in one end of the second coupler output shaft, the other end of the first coupler output shaft is in threaded connection with the third mounting cavity, the end part of the third mounting cavity is in sliding seal with the first coupler output shaft through an end cover, a fourth mounting cavity communicated with the third mounting cavity is axially arranged in the first coupler output shaft, the oil return pipe penetrates through and is communicated with the fourth mounting cavity, an ejector pin assembly used for communicating and blocking the oil return pipe is arranged in the fourth mounting cavity, and the ejector pin assembly is in sliding seal with the fourth mounting cavity, and a gap is reserved between the output shaft of the first coupler and the end face of the third mounting cavity, and hydraulic oil is filled in the gap.

Further, it includes oil pipe and oil pipe down to return oil pipe, the one end and the outer installation cavity of going up oil pipe are linked together, go up oil pipe's the other end and fourth installation cavity intercommunication, oil pipe's one end and fourth installation cavity intercommunication down, and set up with the other end that goes up oil pipe relatively, and oil pipe is led with the annular to oil pipe's the other end down and is linked together.

Further, the thimble assembly includes first spring, first thimble, second thimble and second spring, the fourth installation cavity includes slip chamber and the locking chamber that communicates each other, and the diameter in locking chamber is greater than the slip chamber, first spring supports and leans on the tip setting in slip chamber, and first thimble supports and leans on first spring setting in the slip chamber, has seted up annular groove section on the first thimble, the diameter of first thimble is the same with the diameter in slip chamber, the second thimble is the T font, and the one end of second thimble supports and leans on first thimble setting in the slip chamber, and the other end setting of second thimble is in the locking chamber and with locking chamber sliding seal, and the second spring housing is established on the second thimble in the locking chamber.

Compared with the prior art, the utility model beneficial effect who has is:

the utility model discloses novel structure, the practicality is strong. The utility model provides a continuously variable transmission changes rotational speed and torque under the condition of uninterrupted transmission with the power of input and provides different power transmission for the operating mode of difference. The matching performance with the engine is high, so that the engine is always in the best working state, and the fuel economy is improved. The wear of the gear is extremely low when the gear is output at a high speed for a long time, and the service life is prolonged.

Drawings

Fig. 1 is a schematic diagram of a continuously variable transmission according to the present invention.

Fig. 2 is an internal schematic diagram of a continuously variable transmission according to the present invention.

Fig. 3 is a schematic structural diagram of a continuously variable transmission according to the present invention.

Fig. 4 is a schematic structural diagram of a differential of a continuously variable transmission according to the present invention.

Fig. 5 is a schematic structural diagram of a planetary reducer of a continuously variable transmission according to the present invention.

Fig. 6 is a schematic structural view of a second meshing transmission member of a planetary reduction gear of a continuously variable transmission according to the present invention.

Fig. 7 is a schematic structural diagram of a first view angle of a hydraulic coupling device of a continuously variable transmission according to the present invention.

Fig. 8 is a schematic structural diagram of a second view angle of the hydraulic coupling device of the continuously variable transmission of the present invention.

Fig. 9 is a schematic structural diagram of the connection between the hydraulic coupling device and the torque controller of the continuously variable transmission of the present invention.

Fig. 10 is a schematic structural diagram of a first thimble of a continuously variable transmission according to the present invention.

Fig. 11 is a schematic structural diagram of the first coupler output shaft of the continuously variable transmission according to the present invention.

Fig. 12 is a schematic structural diagram of the second coupler output shaft of the continuously variable transmission according to the present invention.

The labels in the figure are: 1-a first input shaft, 2-a first planet carrier, 3-a first bevel gear, 4-a first planet gear, 5-a second planet gear, 6-a second bevel gear, 7-a sun gear of a first reduction gear set, 8-a planet gear of a first reduction gear set, 9-a second planet carrier, 10-a planet gear of a second reduction gear set, 11-a sun gear of a second reduction gear set, 12-a third planet carrier, 13-an annulus gear, 14-a cam, 15-a cylinder, 16-a piston rod, 17-a first bearing, 18-a second coupler output shaft, 19-a housing, 20-a differential, 21-a connecting shaft, 22-a second bearing, 23-a sun gear of a third reduction gear set, 24-a planet gear of a third reduction gear set, 25-a fourth planet carrier, 26-an annular oil guide pipe, 27-a first spring, 28-a first thimble, 29-a second thimble, 30-a second spring, 31-an oil seal, 32-a brake wheel, 33-a first coupler output shaft, 34-a third bearing, 35-a shifter, 36-a planetary reducer, 37-a hydraulic coupler, 38-a torque controller, 39-a first-stage reduction gear set, 40-a second-stage reduction gear set, 41-a third-stage reduction gear set, 42-an end cover, 43-a first partition plate, 44-an oil return pipe, 45-an outer installation cavity, 46-an inner installation cavity, 47-a bolt, 48-an upper oil pipe, 49-a lower oil pipe and 50-an annular groove section.

Detailed Description

The present invention will be further described with reference to the following examples, which are only some, but not all, of the examples of the present invention. Based on the embodiments in the present invention, other embodiments used by those skilled in the art without creative work belong to the protection scope of the present invention.

Example 1:

as shown in fig. 1 to 3, a continuously variable transmission includes: the device comprises a shell 19, wherein a first installation cavity is formed in the shell 19; the differential 20 is installed in the first installation cavity, the input end of the differential 20 extends out, and the differential is connected with one end of the shell 19 in a shaft mode; a planetary reducer 36, wherein the planetary reducer 36 is installed in the first installation cavity, and one end of the planetary reducer 36 is connected with the output end of the differential 20; a hydraulic coupler 37, wherein the hydraulic coupler 37 is installed in the first installation cavity, and one end of the hydraulic coupler 37 is connected with the other end of the planetary reducer 36; and the torque controller 38 is installed in the first installation cavity, one end of the torque controller 38 is connected with the other end of the hydraulic coupler 37, and the other end of the torque controller 38 penetrates through and extends out of the other end of the shell 19.

As shown in fig. 4, in the present embodiment, the differential 20 includes: first input shaft 1, first bearing 17, first planet carrier 2, first meshing transmission part, second bearing 22 and connecting axle 21, the one end of first input shaft 1 runs through and extends the one end of casing 19, the other end of first input shaft 1 is connected on first planet carrier 2, first meshing transmission part sets up on first planet carrier 2, the one end of connecting axle 21 is connected on first meshing transmission part, the other end of connecting axle 21 runs through planetary reducer 36 and is connected with the second bearing 22 that sets up on hydraulic coupler 37.

In the present embodiment, the first meshing transmission member includes a first planetary gear 4 and a second planetary gear 5 which are oppositely arranged; the first bevel gear 3 and the second bevel gear 6 are oppositely arranged, the first planet carrier 2 comprises an upper mounting end and a lower mounting end, a placing cavity is formed between the upper mounting end and the lower mounting end, the first planet gear 4 is connected with the upper mounting end in an axial mode, the second planet gear 5 is connected with the lower mounting end in an axial mode, the first bevel gear 3 is arranged in the placing cavity, one end of the connecting shaft 21 is fixedly connected with the first bevel gear 3, the second bevel gear 6 is provided with a through avoiding cavity in the axial direction, the second bevel gear 6 is connected to the end portion of the planetary speed reducer 36, the connecting shaft 21 penetrates through the avoiding cavity, the first planet gear 4 is meshed with the first bevel gear 3 and the second bevel gear 6 respectively, and the second planet gear 5 is meshed with the first bevel gear 3 and the second bevel gear 6 respectively.

The first input shaft 1 transmits input power to the first carrier 2, and the power is distributed to the first and second bevel gears 3 and 6 through the first and second

planetary gears

4 and 5 mounted on the first carrier 2. The second bevel gear 6 is rigidly connected with the ring gear 13, the ring gear 13 and the first coupler output shaft 33. That is to say the power distributed to the second bevel gear 6 is directed to the first coupler output shaft 33.

One end of the first input shaft 1 is rigidly connected with the first bevel gear 3, and the other end is fixed on the second bearing 22 through the opening of the bypass cavity of the second bevel gear 6, the second meshing transmission part and the cam 14. The sun gear 7 of the primary reduction gear set is rigidly connected to the first input shaft 1. Thus, the power of the first bevel gear 3 is transmitted to the sun gear 7 of the primary reduction gear set through the first input shaft 1, and the sun gear 7 of the primary reduction gear set is transmitted to the planetary gears 8 of the primary reduction gear set. The planet teeth 8 of the first reduction gear set transfer power to the second planet carrier 9 and to the planet teeth 10 of the next set of planet gears, the second reduction gear set, via the sun teeth 11 of the second reduction gear set, which is rigidly fastened to the second planet carrier 9. The planet teeth 10 of the second reduction gearset transfer power to a third planet carrier 12, and the third planet carrier 12 transfers power to the next set of planet gears, i.e. the planet teeth 24 of the third reduction gearset, through the sun teeth 23 of the third reduction gearset, which is rigidly secured to the third planet carrier 12. The planet teeth 24 of the three stage reduction gear set transmit power to the fourth planet carrier 25, and the fourth planet carrier 25 transmits power to the cam 14.

The power is reduced by the three-stage planetary reduction gear set and finally transmitted to the cam 14. The reduction ratio of a single reduction gear set is generally 1: 2.5 to 1: 5, according to the proportion of 1: 5, calculating by three stages of planetary reduction ratios to be 1: 125, thereby achieving the purpose of reducing the rotating speed and increasing the torque.

As shown in fig. 5 to 6, in this embodiment, the planetary reducer 36 includes an inner gear ring 13 and a second engagement transmission component, a second mounting cavity is formed inside the inner gear ring 13, one end of the inner gear ring 13 is a closed end, the other end of the inner gear ring 13 is an open end, a through hole for the connection shaft 21 to penetrate through is formed in the closed end, the second engagement transmission component is disposed in the second mounting cavity, the connection shaft 21 penetrates through the second engagement transmission component, and the second engagement transmission component is engaged with an inner wall of the second mounting cavity; the open end is connected to an end face of the hydraulic coupler 37.

In this embodiment, the second engagement transmission component includes a first reduction gear set 39, a second reduction gear set 40, a third reduction gear set 41, a second planet carrier 9, a third planet carrier 12, a fourth planet carrier 25 and a cam 14, the first reduction gear set 39 is fixedly connected with the connecting shaft 21, the first reduction gear set 39 transmits power to the second reduction gear set 40 through the second planet carrier 9, the second reduction gear set 40 transmits power to the third reduction gear set 41 through the third planet carrier 12, and the third reduction gear set 41 transmits power to the cam 14 through the fourth planet carrier 25.

As shown in fig. 7 to 8, in the present embodiment, the hydraulic coupler 37 includes: the mounting disc, be equipped with first division board 43 in the mounting disc, first division board 43 is the annular, mutual sealed interior installation cavity 46 and outer installation cavity 45 are separated into with the mounting disc to first division board 43, install the hydro-cylinder 15 that a plurality of equidistance are the setting of cyclic annular distance in outer installation cavity 45, the flexible end of hydro-cylinder 15 is sealed to run through in first division board 43 sets up including installation cavity 46, is equipped with the pulley on the piston rod 16 of hydro-cylinder 15, the pulley is convenient for and cam 14 contact, and 14 circular motion of cam promotes the pulley and then promotes the 16 pistons of piston rod of hydro-cylinder 15 and is reciprocating motion. The cam 14 is arranged in the inner mounting cavity 46, the cam 14 is respectively contacted with the telescopic end of each oil cylinder 15 when rotating, and the inner gear ring 13 is communicated with the inner mounting cavity 46. When the cam 14 and the telescopic end of each oil cylinder 15 of the hydraulic coupler 37 are in a separated state, the power input by the first input shaft 1 is subjected to the resistance of the output end, the power is automatically partially distributed to the first bevel gear 3 by the first planetary gear 4 and the second planetary gear 5, and finally the power is output by the cam 14 with large torque after three-stage planetary reduction.

As shown in fig. 9, increasing the pressure in the oil cylinder 15 by closing the oil outlet of the oil cylinder 15 increases the resistance between the pulley of the piston rod 16 and the cam 14 to achieve engagement of the cam 14 and the hydraulic coupler 37. The engagement process is a process of controlling a difference in the rotational speed of the cam 14 and the hydraulic coupler 37. I.e., the process of converting an input rotational speed to any rotational speed input.

In this embodiment, the hydraulic coupler 37 further includes an annular oil guiding pipe 26 and an oil returning pipe 44, the oil outlet pipe of each oil cylinder 15 penetrates through the side wall of the outer mounting cavity 45 and is communicated with the annular oil guiding pipe 26 disposed outside the outer mounting cavity 45, one end of the oil returning pipe 44 is communicated with the annular oil guiding pipe 26, the other end of the oil returning pipe 44 is communicated with the side wall of the outer mounting cavity 45, and the oil returning pipe 44 penetrates through the torque controller 38.

As shown in fig. 11 to 12, in this embodiment, the torque controller 38 includes a first coupler output shaft 33 and a second coupler output shaft 18, a second partition plate is disposed in the housing 19, one end of the first coupler output shaft 33 penetrates through the second partition plate to be connected to the mounting disk, the first coupler output shaft 33 and the second partition plate are connected through a third bearing 34, a third mounting cavity is opened at one end of the second coupler output shaft 18, the other end of the first coupler output shaft 33 is screwed in the third mounting cavity, an end of the third mounting cavity is slidably sealed with the first coupler output shaft 33 through an end cover 42, and specifically, an oil seal 31 is disposed between the end cover 42 and the first coupler output shaft 33. The other end of the second coupler output shaft 18 penetrates through and extends out of a gear shifter 35 arranged in the shell 19, and the second coupler output shaft 18 is in gear connection with the gear shifter 35 to realize the switching of the forward gear and the reverse gear.

Be equipped with the fourth installation cavity that is linked together with the third installation cavity along the axial in first coupler output shaft 33, return oil pipe 44 and run through and set up with the fourth installation cavity intercommunication, be equipped with the thimble assembly who is used for the intercommunication and blocks back oil pipe 44 in the fourth installation cavity, thimble assembly sliding seal sets up in the fourth installation cavity, reserves the space between the terminal surface of first coupler output shaft 33 and third installation cavity, the space intussuseption is filled with hydraulic oil.

In this embodiment, the oil return pipe 44 includes an upper oil pipe 48 and a lower oil pipe 49, one end of the upper oil pipe 48 is communicated with the outer mounting cavity 45, the other end of the upper oil pipe 48 is communicated with the fourth mounting cavity, one end of the lower oil pipe 49 is communicated with the fourth mounting cavity and is arranged opposite to the other end of the upper oil pipe 48, and the other end of the lower oil pipe 49 is communicated with the annular oil guide pipe 26.

As shown in fig. 10, in this embodiment, the ejector pin assembly includes a first spring 27, a first ejector pin 28, a second ejector pin 29, and a second spring 30, the fourth mounting cavity includes a sliding cavity and a locking cavity that are communicated with each other, a diameter of the locking cavity is greater than that of the sliding cavity, the first spring 27 is disposed at an end portion of the sliding cavity in a abutting manner, the first ejector pin 28 is disposed at the sliding cavity in an abutting manner, an annular groove section 50 is disposed on the first ejector pin 28, a diameter of the first ejector pin 28 is the same as that of the sliding cavity, the second ejector pin 29 is T-shaped, one end of the second ejector pin 29 is disposed at the sliding cavity in an abutting manner, the other end of the second ejector pin 29 is disposed at the locking cavity and is in sliding sealing with the locking cavity, and the second spring 30 is disposed on the second ejector pin 29 in the locking cavity.

When the first thimble 28 is disposed in the sliding cavity and blocks the upper oil pipe 48 and the lower oil pipe 49, the oil path of the oil cylinder 15 is blocked, so that the cam 14 is positioned by the pulley at the end of the piston rod 16 of each oil cylinder 15, the differential 20, the planetary reducer 36, the hydraulic coupler 37 and the torque controller 38 are integrated, the respective internal gear structures do not rotate, and the power input from the first output shaft is 1:1 and is output from the second coupler output shaft 18 of the torque controller 38.

When the resistance of the second coupler output shaft 18 is increased to cause the reduction of the rotation speed, the rotation speed of the first coupler output shaft 33 is driven to be reduced, due to inertia, the first coupler output shaft 33 in threaded connection with the second coupler output shaft continuously keeps rotating at a high speed relative to the first coupler output shaft, and then moves towards the direction of the second coupler output shaft 18 relative to the second coupler output shaft, at the moment, the space between the first coupler output shaft 33 and the side wall of the third installation cavity begins to become smaller, the hydraulic oil in the first coupler output shaft pushes the second thimble 29 to compress the second spring 30 to move towards the first thimble 28, pushes the first thimble 28 to move towards the first spring 27 and compress the first spring 27, and when the annular groove section 50 of the first thimble 28 is communicated with the upper oil pipe 48 and the lower oil pipe 49, the oil outlet oil way begins to be opened to enable the oil at the oil outlet. The piston of the cylinder 15 of the hydraulic coupler 37 starts moving, the cam 14 starts rotating, the difference in rotational speed with the ring gear 13 is pulled, and the torque of the first coupler output shaft 33 rises in accordance with the second coupler output shaft 18. The greater the resistance encountered by second coupler output shaft 18, the greater the stroke of first needle 28, and the greater the proportion of the outlet port that is open. The greater the torque that hydraulic coupler 37 matches to second coupler output shaft 18. The process is automatically matched with the resistance encountered by the running of the automobile.

The brake wheel 32 is sleeved on the first coupler output shaft 33 through a plug 47, the brake wheel 32 is linked with the first ejector pin 28, a key groove for linkage of the first coupler output shaft 33 is formed in the first coupler output shaft 33, and the plug 47 is specifically arranged between the first ejector pin 28 and the second ejector pin 29. When braking, the first thimble 28 is pushed to move towards the first spring 27, and the oil path between the upper oil pipe 48 and the lower oil pipe 49 of the oil outlet is completely opened, so that the piston rod 16 of the oil cylinder 15 is driven by the cam 14 to repeatedly feed oil and discharge oil, the power of the first input shaft 1 is automatically transmitted to the cam 14 from the first bevel gear 3 for no-load output, and the power is cut off.

The key point of the utility model is that the power input by the differential mechanism 20 is divided into two groups. The first group is transmitted to the inner gear ring 13 of the planetary reducer 36 through the second bevel gear 6, and the second bevel gear 6, the inner gear ring 13 of the planetary reducer 36 and the mounting plate of the hydraulic coupler 37 are rigidly connected and directly input to the input end of the torque controller and then output after being transmitted to the mounting plate of the hydraulic coupler 37. The second group is transmitted to the sun gear 7 of the first-stage reduction gear set through the first bevel gear 3, and is transmitted to the cam 14 through the third-stage reduction gear set 41 after being transmitted to the planet gear 8 of the first-stage reduction gear set for speed change, when the oil return pipe 44 at the oil outlet end of the hydraulic coupler 37 is fully opened, the resistance of the power output end acts on the inner gear ring 13, and the second bevel gear 6 of the differential 20 is in a static state. The input power is reduced from the first bevel gear 3 to the high-torque no-load output of the cam 14 through the planetary reducer 36.

When the oil return pipe 44 is slowly closed under the action of the first ejector pin 28, the oil path caliber of the oil outlet of the hydraulic coupler 37 begins to become small, the pressure in the oil cylinder 15 begins to increase, friction force begins to exist between the cam 14 and the pulley of the oil cylinder 15 of the hydraulic coupler 37, the cam 14 begins to drive the output ends of the hydraulic coupler 37 and the inner gear ring 13 to rotate in the same direction, and power output begins to exist. The output torque at the output of torque controller 38 is at a maximum when the proportionally increased resistance to closing of return line 44 reaches a maximum value for the variator ratio of planetary reducer 36. Continuing to close the return line 44, the difference in rotational speed between the hydraulic coupler 37 and the cam 14 decreases, and the torque at the output of the torque controller 38 begins to decrease and the rotational speed increases. The oil return pipe 44 is closed, the hydraulic coupler 37 and the cam 14 are locked, the planetary gear 36 and the differential gear 20 are locked, and the output rotation speed of the torque controller 38 reaches the maximum value. Input and output gear ratio 1:1 sets the torque value at which push torque controller 38 places the needle assembly in operative communication with return line 44 to match the optimum torque value for the engine.

When the vehicle starts to climb the slope or the resistance to forward movement reaches the optimal torque value of the engine, the torque controller 38 starts to work, and pushes the ejector pin assembly to relieve the oil cylinder 15 of the hydraulic coupler 37, so that the speed difference between the hydraulic coupler 37 and the cam 14 is increased, and the rotating speed is lost to obtain the torque. This process varies with the amount of drag encountered by the vehicle in operation. So that the engine always works in the optimum state.

The above description is only exemplary of the present invention and should not be taken as limiting the scope of the present invention, as any modifications, equivalents, improvements and the like made within the spirit and principles of the present invention are intended to be included within the scope of the present invention.

Claims

1. A continuously variable transmission, comprising:

the device comprises a shell (19), wherein a first installation cavity is formed in the shell (19);

the differential (20) is installed in the first installation cavity, the input end of the differential (20) extends out, and the differential is connected to one end of the shell (19) in a shaft mode;

the planetary reducer (36) is installed in the first installation cavity, and one end of the planetary reducer (36) is connected with the output end of the differential (20);

the hydraulic coupler (37) is installed in the first installation cavity, and one end of the hydraulic coupler (37) is connected with the other end of the planetary speed reducer (36);

the torque controller (38) is installed in the first installation cavity, one end of the torque controller (38) is connected with the other end of the hydraulic coupler (37), and the other end of the torque controller (38) penetrates through the other end of the shell (19) and extends out of the other end of the shell.

2. A continuously variable transmission as claimed in claim 1, characterized in that said differential (20) comprises: first input shaft (1), first bearing (17), first planet carrier (2), first meshing transmission part, second bearing (22) and connecting axle (21), the one end of first input shaft (1) is run through and is extended the one end of casing (19), the other end of first input shaft (1) is connected on first planet carrier (2), first meshing transmission part sets up on first planet carrier (2), the one end of connecting axle (21) is connected on first meshing transmission part, the other end of connecting axle (21) runs through planetary reducer (36) and is connected with second bearing (22) that set up on hydraulic coupler (37).

3. A continuously variable transmission as claimed in claim 2, characterized in that said first meshing transmission member comprises first (4) and second (5) planet gears arranged in opposition; a first bevel gear (3) and a second bevel gear (6) which are oppositely arranged, wherein the first planet carrier (2) comprises an upper mounting end and a lower mounting end, and a placing cavity is formed between the upper mounting end and the lower mounting end, the first planet gear (4) is connected with the upper mounting end through a shaft, the second planet gears (5) are connected with the lower mounting end through shafts, the first bevel gears (3) are arranged in the placing cavities, one end of the connecting shaft (21) is fixedly connected with the first bevel gears (3), the second bevel gears (6) are provided with through avoiding cavities along the axial direction, the second bevel gear (6) is connected with the end part of the planetary reducer (36), the connecting shaft (21) penetrates through the avoiding cavity, the first planet gears (4) are respectively meshed with the first bevel gear (3) and the second bevel gear (6), the second planet gears (5) are respectively meshed with the first bevel gears (3) and the second bevel gears (6).

4. The continuously variable transmission according to claim 2, wherein the planetary reducer (36) comprises an inner gear ring (13) and a second engagement transmission component, a second mounting cavity is formed inside the inner gear ring (13), one end of the inner gear ring (13) is a closed end, the other end of the inner gear ring (13) is an open end, a through hole for the connection shaft (21) to penetrate through is formed in the closed end, the second engagement transmission component is arranged in the second mounting cavity, the connection shaft (21) penetrates through the second engagement transmission component, and the second engagement transmission component is engaged with the inner wall of the second mounting cavity; the open end is connected to an end face of a hydraulic coupler (37).

5. The variable transmission of claim 4, wherein the second meshing transmission member comprises a first reduction gear set (39), a second reduction gear set (40), a third reduction gear set (41), a second planet carrier (9), a third planet carrier (12), a fourth planet carrier (25) and a cam (14), the first reduction gear set (39) is fixedly connected with the connecting shaft (21), the first reduction gear set (39) transmits power to the second reduction gear set (40) through the second planet carrier (9), the second reduction gear set (40) transmits power to the third reduction gear set (41) through the third planet carrier (12), and the third reduction gear set (41) transmits power to the cam (14) through the fourth planet carrier (25).

6. A continuously variable transmission as claimed in claim 5, characterized in that said hydraulic coupling (37) comprises: the mounting disc, be equipped with first division board (43) in the mounting disc, mutual sealed interior installation cavity (46) and outer installation cavity (45) are separated into with the mounting disc to first division board (43), install hydro-cylinder (15) that a plurality of equidistant settings in outer installation cavity (45), the flexible end of hydro-cylinder (15) is sealed to run through first division board (43) and sets up in installation cavity (46) including, cam (14) set up in installation cavity (46) including, and cam (14) rotate when respectively with the flexible end contact of each hydro-cylinder (15), ring gear (13) and interior installation cavity (46) are linked together.

7. The variable transmission of claim 6, wherein the hydraulic coupler (37) further comprises an annular oil guide pipe (26) and an oil return pipe (44), the oil outlet pipe of each cylinder (15) is communicated with the annular oil guide pipe (26) disposed outside the outer mounting cavity (45) through the side wall of the outer mounting cavity (45), one end of the oil return pipe (44) is communicated with the annular oil guide pipe (26), the other end of the oil return pipe (44) is communicated with the side wall of the outer mounting cavity (45), and the oil return pipe (44) is disposed through the torque controller (38).

8. The continuously variable transmission according to claim 7, wherein the torque controller (38) comprises a first coupler output shaft (33) and a second coupler output shaft (18), a second partition plate is arranged in the housing (19), one end of the first coupler output shaft (33) penetrates through the second partition plate to be connected with the mounting disc, the first coupler output shaft (33) and the second partition plate are connected through a third bearing (34), a third mounting cavity is formed in one end of the second coupler output shaft (18), the other end of the first coupler output shaft (33) is screwed in the third mounting cavity, the end of the third mounting cavity is in sliding seal with the first coupler output shaft (33) through an end cover (42), a fourth mounting cavity communicated with the third mounting cavity is axially arranged in the first coupler output shaft (33), the oil return pipe (44) penetrates through and is communicated with a fourth installation cavity, a thimble assembly used for communicating and blocking the oil return pipe (44) is arranged in the fourth installation cavity, the thimble assembly is arranged in the fourth installation cavity in a sliding sealing mode, a gap is reserved between the end face of the first coupler output shaft (33) and the end face of the third installation cavity, and hydraulic oil is filled in the gap.

9. The variable transmission of claim 8, wherein the oil return pipe (44) comprises an upper oil pipe (48) and a lower oil pipe (49), one end of the upper oil pipe (48) is communicated with the outer mounting cavity (45), the other end of the upper oil pipe (48) is communicated with the fourth mounting cavity, one end of the lower oil pipe (49) is communicated with the fourth mounting cavity and is arranged opposite to the other end of the upper oil pipe (48), and the other end of the lower oil pipe (49) is communicated with the annular oil guide pipe (26).

10. The stepless transmission of claim 9, wherein the thimble assembly comprises a first spring (27), a first thimble (28), a second thimble (29) and a second spring (30), the fourth installation cavity comprises a sliding cavity and a locking cavity which are communicated with each other, the diameter of the locking cavity is larger than that of the sliding cavity, the first spring (27) is abutted against the end of the sliding cavity, the first thimble (28) is abutted against the first spring (27) and arranged in the sliding cavity, the first thimble (28) is provided with an annular groove section (50), the diameter of the first thimble (28) is the same as that of the sliding cavity, the second thimble (29) is T-shaped, one end of the second thimble (29) is abutted against the first thimble (28) and arranged in the sliding cavity, and the other end of the second thimble (29) is arranged in the locking cavity and is in sliding seal with the locking cavity, the second spring (30) is sleeved on the second ejector pin (29) in the locking cavity.